CN103221242A - Hybrid drive apparatus - Google Patents

Hybrid drive apparatus Download PDF

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Publication number
CN103221242A
CN103221242A CN2011800554933A CN201180055493A CN103221242A CN 103221242 A CN103221242 A CN 103221242A CN 2011800554933 A CN2011800554933 A CN 2011800554933A CN 201180055493 A CN201180055493 A CN 201180055493A CN 103221242 A CN103221242 A CN 103221242A
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CN
China
Prior art keywords
gear
generator
motor
sun
power
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Granted
Application number
CN2011800554933A
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Chinese (zh)
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CN103221242B (en
Inventor
武居康仁
田中住和
熊谷利治
早坂健
吉泽胜裕
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Honda Motor Co Ltd
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Honda Motor Co Ltd
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Priority claimed from JP2010270594A external-priority patent/JP5330362B2/en
Priority claimed from JP2010276735A external-priority patent/JP5437226B2/en
Application filed by Honda Motor Co Ltd filed Critical Honda Motor Co Ltd
Publication of CN103221242A publication Critical patent/CN103221242A/en
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Publication of CN103221242B publication Critical patent/CN103221242B/en
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
    • B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
    • B60K6/50—Architecture of the driveline characterised by arrangement or kind of transmission units
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
    • B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
    • B60K6/22—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs
    • B60K6/36—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs characterised by the transmission gearings
    • B60K6/365—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs characterised by the transmission gearings with the gears having orbital motion
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
    • B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
    • B60K6/22—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs
    • B60K6/38—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs characterised by the driveline clutches
    • B60K6/387—Actuated clutches, i.e. clutches engaged or disengaged by electric, hydraulic or mechanical actuating means
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
    • B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
    • B60K6/42—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by the architecture of the hybrid electric vehicle
    • B60K6/44—Series-parallel type
    • B60K6/445—Differential gearing distribution type
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
    • B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
    • B60K6/42—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by the architecture of the hybrid electric vehicle
    • B60K6/48—Parallel type
    • B—PERFORMING OPERATIONS; TRANSPORTING
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    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
    • B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
    • B60K6/50—Architecture of the driveline characterised by arrangement or kind of transmission units
    • B60K6/54—Transmission for changing ratio
    • B60K6/547—Transmission for changing ratio the transmission being a stepped gearing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/72—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously
    • F16H3/727—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously with at least two dynamo electric machines for creating an electric power path inside the gearing, e.g. using generator and motor for a variable power torque path
    • F16H3/728—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously with at least two dynamo electric machines for creating an electric power path inside the gearing, e.g. using generator and motor for a variable power torque path with means to change ratio in the mechanical gearing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
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    • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
    • F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
    • F16H37/0833—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths
    • F16H37/084—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths at least one power path being a continuously variable transmission, i.e. CVT
    • F16H2037/088—Power split variators with summing differentials, with the input of the CVT connected or connectable to the input shaft
    • F16H2037/0886—Power split variators with summing differentials, with the input of the CVT connected or connectable to the input shaft with switching means, e.g. to change ranges
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    • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
    • F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
    • F16H37/10—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing at both ends of intermediate shafts
    • F16H2037/101—Power split variators with one differential at each end of the CVT
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    • F16H2200/2097—Transmissions using gears with orbital motion comprising an orbital gear set member permanently connected to the housing, e.g. a sun wheel permanently connected to the housing
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/60—Other road transportation technologies with climate change mitigation effect
    • Y02T10/62—Hybrid vehicles
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S903/00—Hybrid electric vehicles, HEVS
    • Y10S903/902—Prime movers comprising electrical and internal combustion motors

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • General Engineering & Computer Science (AREA)
  • Structure Of Transmissions (AREA)
  • Hybrid Electric Vehicles (AREA)

Abstract

A first planetary gear mechanism (P1) transmits the rotation of a first main shaft (13), to which drive force from an engine (E) is input upon engagement of a first clutch (C1), to a main speed-change unit (P2) at the same speed, while transmitting the rotation of the first main shaft (13) to the main speed-change unit (P2) and a first motor generator (MG1) at an increased speed upon engagement of a second clutch (C2). Thus, the range of gear ratio of a transmission (T) can be increased while also increasing the degree of freedom of setting the gear ratio or a step ratio. In addition, the first motor generator (MG1) can be caused to rotate at high speed for increased generation efficiency without requiring a special speed-increasing means. Further, the same-speed transmission of rotation of the first main shaft (13) to the main speed-change unit (P2) eliminates the demand for excessive speed-reduction ratio from the transmission (T), so that friction loss can be reduced and the size of the transmission (T) can be decreased.

Description

Hybrid drive
Technical field
The present invention relates to possess driving engine, the hybrid drive of the 1st motor/generator and change-speed box.
Background technology
According to following patent documentation 1 known such technology: between the input shaft of the bent axle of driving engine and change-speed box, dispose in the motor vehicle driven by mixed power of motor/generator, after the rotation of the bent axle of driving engine being quickened, be passed to the input shaft of motor/generator and change-speed box by sun and planet gear.
In addition, according to following patent documentation 2 known such motor vehicle driven by mixed powers: the bent axle of driving engine is connected with the pinion carrier of sun and planet gear, and the motor/generator of generating usefulness is connected with sun gear, and the motor/generator of traction usefulness is connected with gear ring with drive wheel.
The prior art document
Patent documentation
Patent documentation 1: No. 3815430 communique of Japan's special permission
Patent documentation 2: the open communique WO2009/011328A1 of international application
Summary of the invention
The problem that invention will solve
In addition, in above-mentioned existing technology, because the rotation of the bent axle of driving engine is passed to motor/generator after quickening by sun and planet gear, therefore, when making motor/generator as electrical generator performance function, can improve this rotation generating electricity efficiently, and, when making motor/generator come fire an engine, carry out the failure-free rotation thereby can the torque of motor/generator be increased by sun and planet gear as motor performance function.
; in above-mentioned existing technology; because the rotation of the bent axle of driving engine is passed to change-speed box after quickening by sun and planet gear; therefore; in order to ensure the converter speed ratio of enough big low gear, need utilize the rotating speed after change-speed box will quicken by sun and planet gear is interim to slow down once more, therefore; the reduction ratio that change-speed box is required becomes big, thereby has the setting degree of freedom reduction of change-speed box maximization or converter speed ratio or make driving efficiency reduce such problem because of frictional loss increases.
In addition, when making motor/generator as electrical generator performance function, its rotating speed is high more, can generate electricity efficiently more.In the invention that above-mentioned patent documentation 2 is put down in writing,, therefore can generate electricity efficiently owing to can make the rotation of the bent axle of driving engine quicken the motor/generator of rear drive generating usefulness by sun and planet gear.
; in the invention that above-mentioned patent documentation 2 is put down in writing; only, the motor/generator that will draw usefulness newly is provided with other axle for being configured to slow down; the worry that not only exists number of components or cost to increase; thereby also exist motor/generator to make gear meshing quantity increase the such problem of transmission efficiency reduction because of disalignment configuration traction usefulness; and, cause not having the accelerating action of the output speed of driving engine owing to the motor/generator of disalignment configuration traction usefulness.
The present invention finishes in view of aforesaid situation, and its purpose is, realizes the guaranteeing and the acceleration of motor/generator is driven of suitable converter speed ratio in the change-speed box in mixed power plant simultaneously.
Be used to solve the means of problem
To achieve these goals, the invention provides a kind of hybrid drive, it possesses driving engine, the 1st motor/generator and change-speed box, and it the 1st is characterised in that described change-speed box possesses: input shaft; Output shaft, it disposes abreast with respect to described input shaft; And tween drive shaft, it is configured in from described input shaft on the power transfer path of described output shaft, between described input shaft and described tween drive shaft, be provided with the 1st power transfer path and the 2nd power transfer path, described the 1st power transfer path is by acceleration mechanism and add the speed clutch establishment, described the 2nd power transfer path is not by described acceleration mechanism but by waiting speed clutch to establish, dispose described the 1st motor/generator in the downstream of described acceleration mechanism, dispose main speed changing portion in the downstream of described tween drive shaft.
And, in the invention that possesses the 1st feature, the 1st main shaft 13 and the 2nd of the 1st embodiment, the main shaft 13 of the 3rd embodiment is corresponding to input shaft of the present invention, the countershaft 24 and the 2nd of the 1st embodiment, the countershaft 19 of the 3rd embodiment is corresponding to output shaft of the present invention, the 2nd main shaft 14 and the 2nd of the 1st embodiment, the 2nd tween drive shaft 14 of the 3rd embodiment is corresponding to output shaft of the present invention, the 1st sun and planet gear P1 and the 2nd of the 1st embodiment, the 3rd embodiment add speed drive gear 21, quicken driven gear 22 corresponding to acceleration mechanism of the present invention, the 1st power-transfer clutch C1 of the 1st～the 3rd embodiment is corresponding to the speed clutch that waits of the present invention, the 2nd power-transfer clutch C2 of the 1st～the 3rd embodiment is corresponding to the speed clutch that adds of the present invention, the 2nd sun and planet gear P2 and the 2nd of the 1st embodiment, the sun and planet gear P of the 3rd embodiment is corresponding to main speed changing portion of the present invention.
In addition, the invention provides a kind of hybrid drive, it possesses driving engine, the 1st motor/generator and change-speed box, it the 2nd is characterised in that, on the 1st input shaft of the propulsive effort input of the described driving engine of confession of described change-speed box, dispose the 1st sun and planet gear, the 1st member of described the 1st sun and planet gear always is connected with described the 1st input shaft, the 2nd member of described the 1st sun and planet gear is fixed in housing in the mode that can not rotate, the 3rd member of described the 1st sun and planet gear is connected with described the 1st motor/generator, described the 1st sun and planet gear exports described the 3rd member to after the rotation that is input to described the 1st member from described the 1st input shaft can being quickened, by engaging of the 1st power-transfer clutch that between the main speed changing portion of described the 1st member and described change-speed box, is provided with, with the rotation constant speed of described the 1st input shaft be passed to described main speed changing portion, and, by at the engaging of the 2nd power-transfer clutch that is provided with between described the 3rd member and the described main speed changing portion, after being quickened, the rotation of described the 1st input shaft is passed to described main speed changing portion.
In addition, the of the present invention the 3rd is characterised in that, on the basis of the structure of the 2nd feature, described main speed changing portion is made of the 2nd sun and planet gear, the 1st member of described the 2nd sun and planet gear always is connected with the 2nd motor/generator with the 2nd input shaft, described the 2nd input shaft is embedded in the periphery of described the 1st input shaft in freely the mode of can rotating relatively, the 2nd member of described the 2nd sun and planet gear can be connected with described the 1st member by the 3rd power-transfer clutch, and the 2nd member of described the 2nd sun and planet gear can be fixed in housing by drg, and the 3rd member of described the 2nd sun and planet gear is connected with the output shaft of described change-speed box.
In addition, the of the present invention the 4th is characterised in that, on the basis of the structure of the 3rd feature, described the 1st input shaft and described output shaft dispose parallel to each other, gear that is fixed in the side in described the 1st input shaft and the described output shaft and the gear mesh that is supported on the opposing party in described the 1st input shaft and the described output shaft in freely the mode of can rotating relatively, the described gear that supports in the mode freely of can rotating relatively can combine with the opposing party in described the 1st input shaft and the described output shaft by the 4th power-transfer clutch.
In addition, the of the present invention the 5th is characterised in that, on the basis of the structure of the 3rd or the 4th feature, described the 1st power-transfer clutch and described the 2nd power-transfer clutch and described the 1st motor/generator be disposed at coaxially described the 1st motor/generator interior all sides axially with described the 1st motor/generator position overlapped, described the 3rd power-transfer clutch and described drg and described the 2nd motor/generator be disposed at coaxially described the 2nd motor/generator interior all sides axially and described the 2nd motor/generator position overlapped.
In addition, the of the present invention the 6th is characterised in that, on the basis of any one structure in the 3rd～the 5th feature, described the 1st sun and planet gear and described the 1st motor/generator be disposed at coaxially described the 1st motor/generator interior all sides axially with described the 1st motor/generator position overlapped, described the 2nd sun and planet gear and described the 2nd motor/generator be disposed at coaxially described the 2nd motor/generator interior all sides axially and described the 2nd motor/generator position overlapped.
And, in any one invention in possessing the 2nd～the 6th feature, the 1st main shaft 13 and the 2nd main shaft 14 of the 1st embodiment correspond respectively to the 1st input shaft of the present invention and the 2nd input shaft, the gear ring 15 of the 1st embodiment, sun gear 16 and pinion carrier 17 correspond respectively to the 3rd member of the 1st sun and planet gear of the present invention, the 2nd member and the 1st member, the gear ring 19 of the 1st embodiment, sun gear 20 and pinion carrier 21 correspond respectively to the 2nd member of the 2nd sun and planet gear of the present invention, the 1st member and the 3rd member, the countershaft 24 of the 1st embodiment is corresponding to output shaft of the present invention, master's the 2nd gear 26 of the 1st embodiment is corresponding to the fixing gear of the side in the 1st input shaft and output shaft of the present invention, the gear that pair the 2nd gear 27 of the 1st embodiment is fixed corresponding to the opposing party in the 1st input shaft and output shaft of the present invention, the 2nd sun and planet gear P2 of the 1st embodiment is corresponding to main speed changing portion of the present invention.
In addition, the invention provides a kind of hybrid drive, it possesses driving engine, the 1st motor/generator and change-speed box, and it the 7th is characterised in that described change-speed box possesses: input shaft; Output shaft, it disposes abreast with respect to described input shaft; The 1st tween drive shaft, it is embedded in the periphery of described output shaft in freely the mode of can rotating relatively; And the 2nd tween drive shaft, it is embedded in the periphery of described input shaft in freely the mode of can rotating relatively, the propulsive effort of described driving engine inputs to described input shaft, be located at the 1st gear and the 2nd gear mesh of being located at described output shaft of described input shaft, be passed to this output shaft after thus the rotation of this input shaft being quickened, periphery at described the 2nd tween drive shaft disposes sun and planet gear, the 1st member of described sun and planet gear is connected with the 3rd gear of being located at described the 1st tween drive shaft, the 2nd member of described sun and planet gear is connected with described the 2nd tween drive shaft, the 3rd member of described sun and planet gear is connected with described output shaft, described input shaft can combine with described the 2nd tween drive shaft by the 1st power-transfer clutch, described the 2nd gear can combine with described the 1st tween drive shaft by the 2nd power-transfer clutch, and described the 2nd gear can rotate integratedly with described the 1st motor/generator.
In addition, the of the present invention the 8th is characterised in that, on the basis of the structure of the 7th feature, described the 1st member of described sun and planet gear can combine with described the 2nd tween drive shaft by the 3rd power-transfer clutch, and described the 1st member of described sun and planet gear can combine with housing by drg.
In addition, the of the present invention the 9th is characterised in that, on the basis of the structure of the 7th or the 8th feature, described hybrid drive possesses the 2nd motor/generator that can rotate integratedly with described the 2nd tween drive shaft.
In addition, the of the present invention the 10th is characterised in that, on the basis of any one structure in the 7th～the 9th feature, described the 1st motor/generator is disposed at the outer circumferential side of described the 1st tween drive shaft, described the 2nd gear arrangement is in an axial side of described the 1st motor/generator, and, described the 3rd gear arrangement is in the axial opposite side of described the 1st motor/generator, described the 2nd power-transfer clutch and described the 1st motor/generator be disposed at coaxially described the 1st motor/generator interior all sides axially with described the 1st motor/generator position overlapped.
In addition, the of the present invention the 11st is characterised in that, on the basis of the structure of the 9th or the 10th feature, described the 1st power-transfer clutch and described the 2nd motor/generator be disposed at coaxially described the 2nd motor/generator interior all sides axially with described the 2nd motor/generator position overlapped.
And, in any one invention in possessing the 7th～the 11st feature, the 2nd, the main shaft 13 of the 3rd embodiment is corresponding to input shaft of the present invention, the 2nd, the sun gear 15 of the 3rd embodiment, gear ring 16 and pinion carrier 17 correspond respectively to the 2nd member of sun and planet gear of the present invention, the 1st member and the 3rd member, the 2nd, the countershaft 19 of the 3rd embodiment is corresponding to output shaft of the present invention, the 2nd, the 3rd embodiment add speed drive gear 21 corresponding to the 1st gear of the present invention, the 2nd, the acceleration driven gear 22 of the 3rd embodiment is corresponding to the 2nd gear of the present invention, the 2nd, the acceleration output gear 23 of the 3rd embodiment and acceleration output gear 23 ' corresponding to the 3rd gear of the present invention.
The effect of invention
According to the 1st feature of the present invention, between input shaft and tween drive shaft, be provided with by acceleration mechanism and the 1st power transfer path that adds the speed clutch establishment, not by acceleration mechanism but by waiting the 2nd power transfer path of speed clutch establishment, therefore, to input to main speed changing portion by the rotation that waits the constant speed that speed clutch establishes in low converter speed ratio side, and will input to main speed changing portion by the rotation after adding the acceleration that speed clutch establishes in the transmission ratio side, the scope of the converter speed ratio of change-speed box can be enlarged thus, and the setting degree of freedom of ratio between converter speed ratio or shelves can be enlarged.And, owing to the rotation after the described acceleration can be passed to the 1st motor/generator, therefore, thereby do not need special accelerator module just can make the 1st motor/generator high speed revolution improve generating efficiency.Thus, acceleration mechanism not only can be undertaken the effect that the input speed towards main speed changing portion is quickened, can also undertake the effect that the input speed towards the 1st motor/generator is quickened, need not to be provided with separately the acceleration mechanism that the input speed towards the 1st motor/generator is quickened, thereby can realize the reduction of weight and cost.
In addition, under the situation of the change-speed box that the rotation after the described acceleration can only be input to main speed changing portion, if will quicken rotational delay to becoming the converter speed ratio that needs, then need excessive reduction ratio, thereby there is the worry that frictional loss increases or the change-speed box maximization is such, but,, therefore can realize the reduction of frictional loss and the miniaturization of change-speed box owing to do not need excessive reduction ratio according to the present invention.
In addition, according to the 2nd feature of the present invention, the 1st member of the 1st sun and planet gear that disposes on the 1st input shaft that the propulsive effort for driving engine of change-speed box is imported always is connected with the 1st input shaft, the 2nd member is fixed in housing in the mode that can not rotate, the 3rd member is connected with the 1st motor/generator, therefore, the 1st sun and planet gear can quicken the rotation that is input to the 1st member from the 1st input shaft the back and export the 1st motor/generator to from the 3rd member.Therefore, can engaging by the 1st power-transfer clutch between the main speed changing portion that is located at the 1st member and change-speed box, with the rotation constant speed of the 1st input shaft be passed to main speed changing portion, in addition, can be by being located at engaging of the 2nd power-transfer clutch between the 3rd member and the main speed changing portion, be passed to main speed changing portion after the rotation of the 1st input shaft quickened, and the rotation of described constant speed is inputed to main speed changing portion in low converter speed ratio side, rotation after the transmission ratio side is with described acceleration inputs to main speed changing portion, the scope of the converter speed ratio of change-speed box can be enlarged thus, and the setting degree of freedom of ratio between converter speed ratio or shelves can be enlarged.And, owing to the rotation after the described acceleration can be passed to the 1st motor/generator, therefore, thereby do not need special accelerator module just can make the 1st motor/generator high speed revolution improve generating efficiency.Thus, the 1st sun and planet gear not only can be undertaken the effect that the input speed towards main speed changing portion is quickened, can also undertake the effect that the input speed towards the 1st motor/generator is quickened, need not to be provided with separately the acceleration mechanism that the input speed towards the 1st motor/generator is quickened, thereby can realize the reduction of weight and cost.
In addition, under the situation of the change-speed box that the rotation after the described acceleration can only be input to main speed changing portion, if will quicken rotational delay to becoming the converter speed ratio that needs, then need excessive reduction ratio, thereby there is the worry that frictional loss increases or the change-speed box maximization is such, but,, therefore can realize the reduction of frictional loss and the miniaturization of change-speed box owing to do not need excessive reduction ratio according to the present invention.
In addition, according to the 3rd feature of the present invention, the 1st member of the main speed changing portion that is made of the 2nd sun and planet gear always is connected with the 2nd motor/generator with the 2nd input shaft, the 2nd input shaft is embedded in the periphery of the 1st input shaft in freely the mode of can rotating relatively, the 2nd member can be connected with the 1st member by the 3rd power-transfer clutch, and the 2nd member can be fixed in housing by drg, the 3rd member is connected with the output shaft of change-speed box, therefore, by the 3rd power-transfer clutch and drg are optionally engaged, can make the converter speed ratio of main speed changing portion output produce the two-stage variation, and, by driving the 2nd motor/generator, can realize not using driving engine propulsive effort travel or to travelling that the propulsive effort of driving engine is assisted.
In addition, according to the 4th feature of the present invention, the 1st input shaft and output shaft dispose parallel to each other, gear that is fixed in the side in the 1st input shaft and the output shaft and the gear mesh that is supported on the opposing party in the 1st input shaft and the output shaft in freely the mode of can rotating relatively, the gear that supports in the mode freely of can rotating relatively can combine with the opposing party in the 1st input shaft and the output shaft by the 4th power-transfer clutch, therefore, by making the engaging of the 4th power-transfer clutch, can establish not via the 1st, the gear of the 2nd sun and planet gear, thus the generation of following situation can be prevented: switching in conjunction with the 1st, variable speed control became unstable when the power-transfer clutch of the 2nd sun and planet gear and drg were shifted gears.
In addition, according to the 5th feature of the present invention, the 1st power-transfer clutch and the 2nd power-transfer clutch and the 1st motor/generator are disposed at coaxially the 1st motor/generator interior all sides axially with the 1st motor/generator position overlapped, the 3rd power-transfer clutch and drg and the 2nd motor/generator are disposed at coaxially the 2nd motor/generator interior all sides axially with the 2nd motor/generator position overlapped, thereby therefore can shorten the miniaturization that axial length is realized change-speed box.
In addition, according to the 6th feature of the present invention, the 1st sun and planet gear and the 1st motor/generator are disposed at coaxially the 1st motor/generator interior all sides axially with the 1st motor/generator position overlapped, the 2nd sun and planet gear and the 2nd motor/generator are disposed at coaxially the 2nd motor/generator interior all sides axially with the 2nd motor/generator position overlapped, thereby therefore can shorten the miniaturization that axial length is realized change-speed box.
In addition, according to the 7th feature of the present invention, the 1st gear is arranged at the input shaft for the propulsive effort input of driving engine, be accelerated with the rotation of the 2nd gear of the 1st gear mesh rotation with respect to input shaft, therefore, thereby can drive the 1st motor/generator that rotates integratedly with the 2nd gear with the rotating speed after quickening and to improve generating efficiency, and, because by the 1st, the 2nd gear is passed to the 1st motor/generator after the rotation of input shaft is quickened, therefore, with quicken by sun and planet gear after be passed to the 1st motor/generator situation compare, reduce transmission loss thereby can reduce gear meshing quantity.
In addition, the 2nd gear combines with the 1st tween drive shaft by the 2nd power-transfer clutch, the 1st tween drive shaft is embedded in the periphery of output shaft in freely the mode of can rotating relatively, periphery at the 2nd tween drive shaft is provided with sun and planet gear, the 2nd tween drive shaft is embedded in the periphery of input shaft in freely the mode of can rotating relatively, and the 2nd tween drive shaft combines with input shaft by the 1st power-transfer clutch, the 1st member of sun and planet gear is connected with the 3rd gear of being located at the 1st tween drive shaft, the 2nd member of sun and planet gear is connected with the 2nd tween drive shaft, the 3rd member of sun and planet gear is connected with output shaft, therefore, by will be via the 1st gear, the 2nd gear, the 2nd power-transfer clutch, rotating speed after the 1st tween drive shaft and the 3rd gear quicken, input to sun and planet gear with the rotating speed of the constant speed of having passed through the 1st power-transfer clutch, can between input shaft and output shaft, establish a plurality of gears.
Owing to will be configured for the 2nd gear of the acceleration path of speed change, the 2nd power-transfer clutch, it is coaxial with output shaft that the 1st tween drive shaft and the 3rd gear arrangement become, therefore, not only can make the change-speed box miniaturization, and for being quickened to drive, the 1st motor/generator utilized the acceleration path that is used for speed change, thereby can realize the reduction of cost, and, because the 2nd power-transfer clutch can combine the 2nd gear with the 1st tween drive shaft, therefore, even under the situation that does not need for speed change to quicken, the 2nd power-transfer clutch is not engaged, improve generating efficiency thereby also can make the 1st motor/generator quicken rotation.
In addition, according to the 8th feature of the present invention, the 1st member of sun and planet gear can combine with the 2nd tween drive shaft by the 3rd power-transfer clutch, and the 1st member of sun and planet gear can combine with housing by drg, therefore, by the 3rd power-transfer clutch and drg are optionally engaged, can establish two gears.
In addition, according to the 9th feature of the present invention, owing to be provided with the 2nd motor/generator that can rotate integratedly with the 2nd tween drive shaft, therefore, can make vehicle ' with the propulsive effort of simple structure by the 2nd motor/generator, perhaps the propulsive effort by the 2nd motor/generator comes the propulsive effort of driving engine is assisted, and perhaps the 2nd motor/generator is carried out regenerative brake and reclaims as electric energy with the kinetic energy with vehicle.
In addition, according to the 10th feature of the present invention, with the 2nd gear and the 3rd gear separate configuration in the axial both sides of the 1st motor/generator, the 1st motor/generator is disposed at the periphery of the 1st tween drive shaft, and the 2nd power-transfer clutch and the 1st motor/generator are disposed at coaxially the 1st motor/generator interior all sides with the position of the 1st motor/generator at axial overlap, therefore can shorten the axial length of change-speed box.
In addition, according to the 11st feature of the present invention since the 1st power-transfer clutch and the 2nd motor/generator are disposed at coaxially the 2nd motor/generator interior all sides axially with the 2nd motor/generator position overlapped, so can shorten the axial length of change-speed box.
Description of drawings
Fig. 1 is the skeleton diagram of hybrid drive.(the 1st embodiment)
Fig. 2 is the figure that the establishment state of 1 fast gear is shown.(the 1st embodiment)
Fig. 3 is the figure that the establishment state of 2 fast gears is shown.(the 1st embodiment)
Fig. 4 is the figure that the establishment state of 3 fast gears is shown.(the 1st embodiment)
Fig. 5 is the figure that the establishment state of 4 fast gears is shown.(the 1st embodiment)
Fig. 6 is the figure that the establishment state of 5 fast gears is shown.(the 1st embodiment)
Fig. 7 is the speed line chart of change-speed box.(the 1st embodiment)
Fig. 8 is the 1st of change-speed box～the 4th power-transfer clutch and the table that engages of drg.(the 1st embodiment)
Fig. 9 is the skeleton diagram of hybrid drive.(the 2nd embodiment)
Figure 10 is the figure that the establishment state of 1 fast gear is shown.(the 2nd embodiment)
Figure 11 is the figure that the establishment state of 2 fast gears is shown.(the 2nd embodiment)
Figure 12 is the figure that the establishment state of 3 fast gears is shown.(the 2nd embodiment)
Figure 13 is the figure that the establishment state of 4 fast gears is shown.(the 2nd embodiment)
Figure 14 is the speed line chart of change-speed box.(the 2nd embodiment)
Figure 15 is the 1st of change-speed box～the 3rd power-transfer clutch and the table that engages of drg.(the 2nd embodiment)
Figure 16 is the skeleton diagram of hybrid drive.(the 3rd embodiment)
Figure 17 is the figure that the establishment state of 2 fast gears is shown.(the 3rd embodiment)
Figure 18 is the figure that the establishment state of 3 fast gears is shown.(the 3rd embodiment)
Figure 19 is the speed line chart of change-speed box.(the 3rd embodiment)
Figure 20 is the 1st of change-speed box～the 4th power-transfer clutch and the table that engages of drg.(the 3rd embodiment)
Label declaration
［ the 1st embodiment ］
13: the 1 main shafts (input shaft, the 1st input shaft);
14: the 2 main shafts (tween drive shaft, the 2nd input shaft);
15: gear ring (the 3rd member of the 1st sun and planet gear);
16: sun gear (the 2nd member of the 1st sun and planet gear);
17: pinion carrier (the 1st member of the 1st sun and planet gear);
19: gear ring (the 2nd member of the 2nd sun and planet gear);
20: sun gear (the 1st member of the 2nd sun and planet gear);
21: pinion carrier (the 3rd member of the 2nd sun and planet gear);
24: countershaft (output shaft);
26: main the 2nd gear (being fixed in the gear of the side in the 1st input shaft and the output shaft);
27: secondary the 2nd gear (being fixed in the opposing party's gear in the 1st input shaft and the output shaft);
31: housing;
B1: drg;
C1: the 1st power-transfer clutch (waiting speed clutch);
C2: the 2nd power-transfer clutch (adding speed clutch);
C3: the 3rd power-transfer clutch;
C4: the 4th power-transfer clutch;
E: driving engine;
P1: the 1st sun and planet gear (acceleration mechanism);
P2: the 2nd sun and planet gear (main speed changing portion);
MG1: the 1st motor/generator;
MG2: the 2nd motor/generator;
T: change-speed box;
［ the 2nd and the 3rd embodiment ］
13: main shaft (input shaft);
14: the 2 tween drive shafts (tween drive shaft);
15: sun gear (the 2nd member of sun and planet gear);
16: gear ring (the 1st member of sun and planet gear);
17: pinion carrier (the 3rd member of sun and planet gear);
19: countershaft (output shaft);
20: the 1 tween drive shafts;
21: add speed drive gear (acceleration mechanism, the 1st gear);
22: quicken driven gear (acceleration mechanism, the 2nd gear);
23: quicken output gear (the 3rd gear);
23 ': acceleration output gear (the 3rd gear);
30: housing;
B1: drg;
C1: the 1st power-transfer clutch (waiting speed clutch);
C2: the 2nd power-transfer clutch (adding speed clutch);
C3: the 3rd power-transfer clutch;
E: driving engine;
P: sun and planet gear (main speed changing portion);
MG1: the 1st motor/generator;
MG2: the 2nd motor/generator;
T: change-speed box.
The specific embodiment
Below, based on accompanying drawing embodiments of the present invention are described.
The 1st embodiment
Below, based on Fig. 1～Fig. 8 the 1st embodiment of the present invention is described.
As shown in Figure 1, the change-speed box T of motor vehicle driven by mixed power possesses the 1st main shaft 13, the 1 main shafts 13 are connected in driving engine E coaxially by bumper 12 bent axle 11, the 2 main shafts 14 can counterrotating mode to be embedded in the periphery of the 1st main shaft 13.The 1st sun and planet gear P1 in the acceleration usefulness of the axle head setting of the side opposite with driving engine E of the 1st main shaft 13 possesses: gear ring 15, and its rotor with the 1st motor/generator MG1 is connected; Sun gear 16, it is fixed in housing 31; Pinion carrier 17, it is fixed in the 1st main shaft 13; And a plurality of miniature gears 18..., it is supported in pinion carrier 17 in the mode that can rotate freely, and meshes with described gear ring 15 and described sun gear 16 simultaneously.The 2nd main shaft 14 by the 1st power-transfer clutch C1 can with pinion carrier 17 promptly the 1st main shaft 13 combine, and the 2nd main shaft 14 can be that the rotor of the 1st motor/generator MG1 combines with gear ring 15 by the 2nd power-transfer clutch C2.
The 2nd sun and planet gear P2 that uses in the speed change of the periphery setting of the 2nd main shaft 14 possesses: gear ring 19; Sun gear 20, it is fixed in the 2nd main shaft 14; Pinion carrier 21; And a plurality of miniature gears 22..., it is supported in pinion carrier 21 in the mode that can rotate freely, and meshes with described gear ring 19 and described sun gear 20 simultaneously.Gear ring 19 can combine with rotor and the 2nd main shaft 14 of the 2nd motor/generator MG2 by the 3rd power-transfer clutch C3, and gear ring 19 can combine with housing 31 by drg B1.
Be fixed in master's the 1st gear 23 and pair the 1st gear 25 engagements of being fixed in countershaft 24 of the pinion carrier 21 of the 2nd sun and planet gear P2.In addition, main the 2nd gear 26 and pair the 2nd gear 27 engagements of being fixed in countershaft 24, this main the 2nd gear 26 can combine with the 1st main shaft 13 by the 4th power-transfer clutch C4.And, be fixed in the final driven wheel 28 of countershaft 24 and final driven gear 29 engagements of being fixed in diff D, about drive wheel W, W be connected with the axle drive shaft 30,30 that from about diff D, extends.
Next, the effect to the 1st embodiment of the present invention that possesses said structure describes.
According to Fig. 1 and Fig. 7 as can be known, if make the 1st power-transfer clutch C1 engaging, then the 1st main shaft 13 directly links by pinion carrier 17 and the 2nd main shaft 14 of the 1st sun and planet gear P1, so the 2nd main shaft 14 and the 1st main shaft 13 rotate with same rotating speed.In addition, if make the 2nd power-transfer clutch C2 engaging, the gear ring 15 that then sun gear 16 is fixed in the 1st sun and planet gear P1 of housing 31 combines with the 2nd main shaft 14, therefore, the rotation that inputs to pinion carrier 17 from the 1st main shaft 13 is accelerated and exports to gear ring 15, thereby makes the rotating speed acceleration of the rotating speed of the 2nd main shaft 14 with respect to the 1st main shaft 13.
If make drg B1 engaging, then the gear ring 19 of the 2nd sun and planet gear P2 is fixed in housing 31, exports pinion carrier 21 to after therefore the rotation that inputs to sun gear 20 from the 2nd main shaft 14 is decelerated.In addition, if make the 3rd power-transfer clutch C3 engaging, then gear ring 19 combines with sun gear 20 by the 2nd main shaft 14, thereby makes the 2nd sun and planet gear P2 become lock-out state, and the rotation of the 2nd main shaft 14 directly exports pinion carrier 21 to.
Therefore, by to the engaging of the 1st～the 3rd power-transfer clutch C1～C3 and drg B1/do not engage and make up, can carry out being passed to countershaft 24 after the speed change to the rotation of the 1st main shaft 13 with various converter speed ratios.
The 1st sun and planet gear P1, the 1st power-transfer clutch C1 and the 2nd power-transfer clutch C2 that are accommodated in interior all sides of the 1st motor/generator MG1 are configured to be accommodated in the axial width of the 1st motor/generator MG1, in addition, the 2nd sun and planet gear P2, the 3rd power-transfer clutch C3 and the drg B1 that is accommodated in interior all sides of the 2nd motor/generator MG2 is configured to be accommodated in the axial width of the 2nd motor/generator MG2.
Below, the establishment state separately of each gear of 1 speed～5 speed is described particularly.
Thereby Fig. 2 shows the state that makes the 1st power-transfer clutch C1 and drg B1 engaging establish 1 fast gear.The rotation of driving engine E is passed to drive wheel W, W with the path of sun gear 20, miniature gears 22... and pinion carrier 21 → master's the 1st gear 23 → pair the 1st gear 25 → countershaft 24 → final driven wheel 28 → final driven gear 29 → diff D → axle drive shaft 30,30 of pinion carrier 17 → the 1st power-transfer clutch C1 → the 2nd main shaft 14 → the 2nd sun and planet gear P2 of bent axle 11 → bumper 12 → the 1st main shaft 13 → the 1st sun and planet gear P1.
At this moment, neither slow down at the 1st sun and planet gear P1 and also not quicken, slow down, establish 1 fast gear thus at the 2nd sun and planet gear P2.
Thereby Fig. 3 shows the state that makes the 2nd power-transfer clutch C2 and drg B1 engaging establish 2 fast gears.The rotation of driving engine E is passed to drive wheel W, W with the path of sun gear 20, miniature gears 22... and pinion carrier 21 → master's the 1st gear 23 → pair the 1st gear 25 → countershaft 24 → final driven wheel 28 → final driven gear 29 → diff D → axle drive shaft 30,30 of pinion carrier 17, miniature gears 18... and gear ring 15 → the 2nd power-transfer clutch C2 → the 2nd main shaft 14 → the 2nd sun and planet gear P2 of bent axle 11 → bumper 12 → the 1st main shaft 13 → the 1st sun and planet gear P1.
At this moment, quicken, slow down, establish the converter speed ratio 2 fast gears littler thus than 1 fast gear at the 2nd sun and planet gear P2 at the 1st sun and planet gear P1.
Thereby Fig. 4 shows the state that makes the 4th power-transfer clutch C4 engaging establish 3 fast gears.The rotation of driving engine E is passed to drive wheel W, W with the path of bent axle 11 → bumper 12 → the 1st main shaft 13 → the 4th power-transfer clutch C4 → master's the 2nd gear 26 → pair the 2nd gear 27 → countershaft 24 → final driven wheel 28 → final driven gear 29 → diff D → axle drive shaft 30,30.
At this moment, both being rotated in of the 1st main shaft 13 is not passed to countershaft 24 under the situation via the 2nd sun and planet gear P2 via the 1st sun and planet gear P1 yet, but established the converter speed ratio 3 fast gears littler than 2 fast gears by main the 2nd gear 26 with the setting of the number of teeth of secondary the 2nd gear 27.
Thereby Fig. 5 shows the state that makes the 1st power-transfer clutch C1 and the 3rd power-transfer clutch C3 engaging establish 4 fast gears.The path of pinion carrier 21 → master's the 1st gear 23 → pair the 1st gear 25 → countershaft 24 → final driven wheel 28 → final driven gear 29 → diff D → axle drive shaft 30,30 of the 2nd sun and planet gear P2 that the rotation of driving engine E locks with the engaging of pinion carrier 17 → the 1st power-transfer clutch C1 → the 2nd main shaft 14 of bent axle 11 → bumper 12 → the 1st main shaft 13 → the 1st sun and planet gear P1 → by the 3rd power-transfer clutch C3 is passed to drive wheel W, W.
At this moment, neither quicken also not slow down, also neither quicken also not slow down, establish the converter speed ratio 4 fast gears littler thus than 3 fast gears at the 2nd sun and planet gear P2 at the 1st sun and planet gear P1.
Thereby Fig. 6 shows the state that makes the 2nd power-transfer clutch C2 and the 3rd power-transfer clutch C3 engaging establish 5 fast gears.The path of pinion carrier 21 → master's the 1st gear 23 → pair the 1st gear 25 → countershaft 24 → final driven wheel 28 → final driven gear 29 → diff D → axle drive shaft 30,30 of the 2nd sun and planet gear P2 that the rotation of driving engine E locks with the engaging of pinion carrier 17, miniature gears 18... and gear ring 15 → the 2nd power-transfer clutch C2 → the 2nd main shaft 14 of bent axle 11 → bumper 12 → the 1st main shaft 13 → the 1st sun and planet gear P1 → by the 3rd power-transfer clutch C3 is passed to drive wheel W, W.
At this moment, quicken, neither quicken also not slow down, establish the converter speed ratio 5 fast gears littler thus than 4 fast gears at the 2nd sun and planet gear P2 at the 1st sun and planet gear P1.
According to Fig. 8 as can be known, the 2nd power-transfer clutch C2 and drg B1 engaging when 2 fast gears, the 1st power-transfer clutch C1 and the 3rd power-transfer clutch C3 engaging when 4 fast gears.If consider that when not having 3 fast gears from 2 fast gear direct changes be the 4 fast gears or the situation that is 2 fast gears from 4 fast gear direct changes, need then to carry out simultaneously that the 1st power-transfer clutch C1 combines with switching between the 2nd power-transfer clutch C2 and the 3rd power-transfer clutch C3 combines with switching between the drg B1, therefore, as long as have trickle error the opportunity of this switching combination, just may produce the variable speed control unsure state., according to present embodiment,, can eliminate above-mentioned unfavorable condition by making the 3 fast gears that do not need to switch in conjunction with the 1st～the 3rd power-transfer clutch C1～C3 and drg B1 between 2 fast gears and 4 fast gears.
(zero) expression among Fig. 8, no matter the 3rd power-transfer clutch C3 and drg B1 engaging still do not engage, all the establishment to 3 fast gears does not exert an influence.Therefore, when shifting up to 4 fast gears, make the 3rd power-transfer clutch C3 engaging in advance from 3 fast gears, under this state, make the 1st power-transfer clutch C1 engaging, establish 4 fast gears thus, like this, even without controlling the opportunity of switching combination accurately, also can realize shifting up smoothly.Equally, from the fast gear of 3 fast gear downshifts to 2 time, make drg B1 engaging in advance, under this state, make the 2nd power-transfer clutch C2 engaging, establish 2 fast gears thus, like this, even without controlling the opportunity of switching combination accurately, also can realize downshift smoothly.
The 1st motor/generator MG1 is rotated by means of the propulsive effort of driving engine E, thus mainly as electrical generator performance function.If driving engine E is in the operation process, then no matter be in the 1st power-transfer clutch C1 engaging state, or the state of the 2nd power-transfer clutch C2 engaging, or the 1st, the 2nd power-transfer clutch C1, C2 not have the state that engages, the rotation of the 1st main shaft 13 all is passed to the 1st motor/generator MG1 after being quickened by the 1st sun and planet gear P1, therefore, thus can at high speed drive the 1st motor/generator MG1 improves generating efficiency.
Like this, after quickening the rotation of the 1st main shaft 13, utilization is passed to the 1st sun and planet gear P1 of the 2nd main shaft 14, can be to quickening towards the input rotation of the 1st motor/generator MG1, therefore do not need to be used for the special acceleration mechanism that quickens towards the input rotation of the 1st motor/generator MG1, thereby can help the reduction of weight and cost.
And,, thereby then can utilize the propulsive effort of the 1st motor/generator MG1 to make bent axle 11 rotations make driving engine E starting if make the 1st motor/generator MG1 bring into play function as motor.If drive the 1st motor/generator MG1 under the state that makes the 1st power-transfer clutch C1 and the 2nd power-transfer clutch C2 all not have to engage in order in the driving process of vehicle, to make driving engine E starting, then it is rotated in by the 1st sun and planet gear P1 deceleration back and is passed to bent axle 11 from the 1st main shaft 13, thereby therefore can make bent axle 11 rotate the startability that improves driving engine E with big torque.
The 2nd motor/generator MG2 and the 2nd main shaft 14 mainly as motor performance function directly link, therefore, no matter be under the situation of having established which gear, can both make vehicle ' by the propulsive effort of the 2nd motor/generator MG2 or utilize the propulsive effort of the 2nd motor/generator MG2 to come the propulsive effort of auxiliary engine E.In addition, the propulsive effort from drive wheel W, W side back transfer makes the 2nd motor/generator MG2 bring into play function as electrical generator when car retardation if utilize, and then the kinetic energy of vehicle can be reclaimed as electric energy.
Next, the action effect to the 1st embodiment of the present invention describes.
If make the 1st power-transfer clutch C1 engaging, then the 1st main shaft 13 and the 2nd main shaft 14 directly link, thereby make the rotation of the 1st main shaft 13 be passed to the 2nd main shaft 14 with identical speed, if make the 2nd power-transfer clutch C2 engaging, then being rotated in of the 1st main shaft 13 is passed to the 2nd main shaft 14 after the 1st sun and planet gear P1 acceleration, therefore, by the 1st, the 2nd power-transfer clutch C1, C2 are optionally engaged, the scope of the converter speed ratio of change-speed box T can be enlarged, and the setting degree of freedom of ratio between converter speed ratio or shelves can be enlarged.And, owing to be passed to the 1st motor/generator MG1 after the rotation of the 1st main shaft 13 can being quickened, therefore, thereby do not need special accelerator module just can make the 1st motor/generator MG1 high speed revolution improve generating efficiency.Like this, the 1st sun and planet gear P1 is not only undertaking the effect that the input speed towards the 2nd sun and planet gear P2 is quickened, also undertake the effect that the input speed towards the 1st motor/generator MG1 is quickened, therefore can realize the reduction of weight and cost.
In addition, if the rotation after supposing to will speed up is input to the 2nd sun and planet gear P2 of change-speed box T, then extremely can obtain the converter speed ratio of needs for the rotational delay after will quickening, need excessive reduction ratio, thereby there is the worry that frictional loss increases or change-speed box T maximization is such, but,, therefore can realize the reduction of frictional loss and the miniaturization of change-speed box T owing to do not need excessive reduction ratio according to present embodiment.
In addition, in the 2nd sun and planet gear P2 of the main speed changing portion that constitutes change-speed box T, if make the 3rd power-transfer clutch C3 engaging, then can export the rotation of the 2nd main shaft 14 to countershaft 24 sides with identical speed, if make drg B1 engaging, export countershaft 24 sides to after then the rotation of the 2nd main shaft 14 can being slowed down, therefore, by the combination of two grades of converter speed ratios among the 1st sun and planet gear P1 and two grades of converter speed ratios among the 2nd sun and planet gear P2, can obtain four-speed gear shift than (1 speed, 2 speed, 4 speed and 5 speed).And, because the 2nd motor/generator MG2 directly is linked to the 2nd main shaft 14, therefore, can realize not using that the propulsive effort based on the 2nd motor/generator MG2 of the propulsive effort of driving engine E realizes travels or the propulsive effort by the 2nd motor/generator MG2 comes travelling that the propulsive effort of driving engine E is assisted.
In addition, dispose the 1st main shaft 13 and countershaft 24 in parallel to each other, make main the 2nd gear 26 and pair the 2nd gear 27 engagements of being fixed in countershaft 24, this main the 2nd gear 26 can combine with the 1st main shaft 13 by the 4th power-transfer clutch C4, therefore, by making the 4th power-transfer clutch C4 engaging, can establish not 3 fast gears via the 1st, the 2nd sun and planet gear P1, P2, thereby can prevent the generation of following situation: variable speed control becomes unstable when shifting gears in conjunction with the 1st～the 3rd power-transfer clutch C1～C3 of the 1st, the 2nd sun and planet gear P1, P2 and drg B1 switching.
In addition, the 1st sun and planet gear P1, the 1st power-transfer clutch C1 and the 2nd power-transfer clutch C2 are disposed at interior all sides of the 1st motor/generator MG1 in the mode in the axial width that is accommodated in the 1st motor/generator MG1, therefore, thus can shorten the miniaturization that axial size realizes change-speed box T.Equally, the 2nd sun and planet gear P2, the 3rd power-transfer clutch C3 and drg B1 are disposed at interior all sides of the 2nd motor/generator MG2 in the mode in the axial width that is accommodated in the 2nd motor/generator MG2, therefore, thus can shorten the miniaturization that axial size realizes change-speed box T.
The 2nd embodiment
Below, based on Fig. 9～Figure 15 the 2nd embodiment of the present invention is described.And the label that uses in the 2nd embodiment is with respect to (independent with reference to the label that uses among Fig. 1～Fig. 8), identical label is not necessarily indicated cooresponding structural elements at the 1st embodiment.In addition, (label with reference to use among Figure 16～Figure 20) is shared, and identical label is indicated cooresponding structural elements at this 2nd embodiment and the 3rd embodiment described later.
As shown in Figure 9, the four-speed change-speed box T of motor vehicle driven by mixed power possesses main shaft 13, and this main shaft 13 is connected in driving engine E coaxially by bumper 12 bent axle 11, the 2 tween drive shafts 14 are can counterrotating mode to be embedded in the periphery of main shaft 13.The 2nd tween drive shaft 14 can combine with main shaft 13 by the 1st power-transfer clutch C1, and the 2nd tween drive shaft 14 is connected with the rotor of the 2nd motor/generator MG2.
The sun and planet gear P that uses in the speed change of the periphery setting of main shaft 13 and the 2nd tween drive shaft 14 possesses: sun gear 15; Gear ring 16; Pinion carrier 17; And a plurality of miniature gears 18..., it is supported in pinion carrier 17 in the mode that can rotate freely, and meshes with described sun gear 15 and described gear ring 16 simultaneously.Sun gear 15 is fixed in the 2nd tween drive shaft 14, and gear ring 16 can combine with housing 30 by drg B1, and can combine with the 2nd tween drive shaft 14 by the 3rd power-transfer clutch C3.
The 1st tween drive shaft 20 is can counterrotating mode to be embedded in the periphery of the countershaft 19 of change-speed box T.What be fixed in main shaft 13 adds speed drive gear 21 and acceleration driven gear 22 engagements that are supported on the 1st tween drive shaft 20 in freely the mode of can rotating relatively, be fixed in the acceleration output gear 23 of the 1st tween drive shaft 20 and speed change input gear 24 engagements of the periphery of the gear ring 16 that is integrally formed in sun and planet gear P, be fixed in the 1st speed change output gear 25 and the 2nd speed change output gear 26 engagements of being fixed in countershaft 19 of the pinion carrier 17 of sun and planet gear P.Quicken driven gear 22 and be connected, and acceleration driven gear 22 can combine with the 1st tween drive shaft 20 by the 2nd power-transfer clutch C2 with the rotor of the 1st motor/generator MG1.
And, be fixed in the final driven wheel 27 of countershaft 19 and final driven gear 28 engagements of being fixed in diff D, about drive wheel W, W be connected with the axle drive shaft 29,29 that from about diff D, extends.
Quicken driven gear 22 and quicken output gear 23 separate configuration, be configured in the position at axial overlap with respect to the 1st motor/generator MG1 at the 2nd power-transfer clutch C2 of the coaxial setting of interior all sides of the 1st motor/generator MG1 in the axial both sides of the 1st motor/generator MG1.In addition, the 1st power-transfer clutch C1 in the coaxial setting of interior all sides of the 2nd motor/generator MG2 is configured in the position at axial overlap with respect to the 2nd motor/generator MG2.
Next, the effect to the 2nd embodiment of the present invention that possesses said structure describes.
According to Fig. 9 and Figure 14 as can be known, if make the 1st power-transfer clutch C1 engaging, then main shaft 13 and the 2nd tween drive shaft 14 directly link, so the 2nd tween drive shaft 14 and main shaft 13 rotate with same rotating speed.In addition, if make the 2nd power-transfer clutch C2 engaging, then the rotation of main shaft 13 is via adding the gear ring 16 that speed drive gear 21, acceleration driven gear the 22, the 2nd power-transfer clutch C2, the 1st tween drive shaft 20, acceleration output gear 23 and speed change input gear 24 are passed to sun and planet gear P.At this moment, the number of teeth of quickening driven gear 22 owing to the ratio of number of teeth that adds speed drive gear 21 is big, therefore, makes the rotation of gear ring 16 be accelerated with respect to the rotation of main shaft 13.
And, the ratio of number of teeth that adds speed drive gear 21 and acceleration driven gear 22 must be set at acceleration, but the ratio of number of teeth that quickens output gear 23 and speed change input gear 24 both can be a constant speed also can be to quicken, and the ratio of number of teeth that quickens output gear 23 and speed change input gear 24 in addition also can be can be with by not adding speed drive gear 21 and quickening the deceleration of the degree that acceleration that driven gear 22 realizes offsets.
If make drg B1 engaging, then the gear ring 16 of sun and planet gear P is fixed in housing 30, exports i.e. the 1st speed change output gear 25 of pinion carrier 17 to after therefore the rotation that is input to sun gear 15 from the 2nd tween drive shaft 14 is decelerated.In addition, if make the 3rd power-transfer clutch C3 engaging, then gear ring 16 combines with sun gear 15 by the 2nd tween drive shaft 14, makes sun and planet gear P become lock-out state thus, thereby the rotation of the 2nd tween drive shaft 14 directly exports i.e. the 1st speed change output gear 25 of pinion carrier 17 to.
Therefore, by to the engaging of the 1st～the 3rd power-transfer clutch C1～C3 and drg B1/do not engage and make up, can carry out being passed to countershaft 19 after the speed change to the rotation of main shaft 13 with various converter speed ratios.
Below, with reference to Figure 14 and Figure 15 the establishment state separately of each gear of 1 speed～4 speed is described particularly.
Thereby Figure 10 shows the state that makes the 1st power-transfer clutch C1 and drg B1 engaging establish 1 fast gear.The rotation of driving engine E is passed to drive wheel W, W with the path of sun gear 15, miniature gears 18... and pinion carrier 17 → the 1st speed change output gear 25 → the 2nd speed change output gear 26 → countershaft 19 → final driven wheel 27 → final driven gear 28 → diff D → axle drive shaft 29,29 of bent axle 11 → bumper 12 → main shaft 13 → the 1st power-transfer clutch C1 → the 2nd tween drive shaft 14 → sun and planet gear P.
At this moment, P slows down at sun and planet gear, establishes 1 fast gear thus.
Thereby Figure 11 shows the state that makes the 1st power-transfer clutch C1 and the 3rd power-transfer clutch C3 engaging establish 2 fast gears.Owing to thereby the 3rd power-transfer clutch C3 engaging makes the sun gear 15 of sun and planet gear P and gear ring 16 combinations make sun and planet gear P become lock-out state, therefore, the rotation of driving engine E is passed to drive wheel W, W with the path of sun and planet gear P → the 1st speed change output gear 25 → the 2nd speed change output gear 26 → countershaft 19 → final driven wheel 27 → final driven gear 28 → diff D → axle drive shaft 29,29 of bent axle 11 → bumper 12 → main shaft 13 → the 1st power-transfer clutch C1 → the 2nd tween drive shaft 14 → lock-out state.
At this moment, both do not quickened not slow down yet, established the converter speed ratio 2 fast gears littler thus than 1 fast gear at sun and planet gear P.
Thereby Figure 12 shows the state that makes the 1st power-transfer clutch C1 and the 2nd power-transfer clutch C2 engaging establish 3 fast gears.Because the 2nd power-transfer clutch C2 engaging, make the rotation of main shaft 13 by by adding speed drive gear 21, quicken driven gear the 21, the 2nd power-transfer clutch C2, the 1st tween drive shaft 20, quickening the gear ring 16 that acceleration path that output gear 23 and speed change input gear 24 constitute is passed to sun and planet gear P, the rotation of gear ring 16 is accelerated with respect to the rotation of main shaft 13, on the other hand, because the 1st power-transfer clutch C1 engaging makes main shaft 13 directly link by the sun gear 15 of the 2nd tween drive shaft 14 with sun and planet gear P.Consequently, the rotation of driving engine E is passed to drive wheel W, W with the path of sun gear 15, miniature gears 18... and pinion carrier 17 → the 1st speed change output gear 25 → the 2nd speed change output gear 26 → countershaft 19 → final driven wheel 27 → final driven gear 28 → diff D → axle drive shaft 29,29 of bent axle 11 → bumper 12 → main shaft 13 → the 1st power-transfer clutch C1 → the 2nd tween drive shaft 14 → sun and planet gear P.
At this moment, P quickens at sun and planet gear, establishes the converter speed ratio 3 fast gears littler than 2 fast gears thus.
Thereby Figure 13 shows the state that makes the 2nd power-transfer clutch C2 and the 3rd power-transfer clutch C3 engaging establish 4 fast gears.Owing to thereby the 3rd power-transfer clutch C3 engaging makes the sun gear 15 of sun and planet gear P and gear ring 16 combinations make sun and planet gear P become lock-out state, therefore, the rotation of driving engine E is with sun and planet gear P → the 1st speed change output gear 25 → the 2nd speed change output gear 26 → countershaft 19 → final driven wheel 27 → final driven gear 28 → diff D → axle drive shaft 29 of bent axle 11 → bumper 12 → main shaft 13 → add speed drive gear 21 → acceleration driven gear 22 → the 2nd power-transfer clutch C2 → the 1st tween drive shaft 20 → acceleration output gear 23 → speed change input gear 24 → lock-out state, 29 path is passed to drive wheel W, W.
At this moment, neither quicken also not slow down, but, establish the converter speed ratio 4 fast gears littler thus than 3 fast gears by adding speed drive gear 21 and quickening driven gear 22 and quicken at sun and planet gear P.
Next, the action effect to the 2nd embodiment of the present invention describes.
Main shaft 13, the accelerator module that adds speed drive gear 21, quickens driven gear the 22, the 1st tween drive shaft 20 and quicken output gear 23 formation parallel shafts, it can quicken the rotation of main shaft 13 back and transmit sun and planet gear P, and, thereby can be with the acceleration driven gear 22 all-in-one-pieces 1st motor/generator MG1 raising generating efficiency of the driving of the rotating speed after quickening with this accelerator module.At this moment, owing to be passed to the 1st motor/generator MG1 after driven gear 22 quickens the rotation of main shaft 13 by adding speed drive gear 21 and quickening, therefore, compare with the situation that is passed to the 1st motor/generator MG1 after sun and planet gear by special use quickens, improve transmission efficiency thereby can reduce gear meshing quantity.
And,, thereby then can utilize the propulsive effort of the 1st motor/generator MG1 to make bent axle 11 rotations make driving engine E starting if make the 1st motor/generator MG1 bring into play function as motor.At this moment, therefore the rotation of the 1st motor/generator MG1, improves startability thereby can bent axle 11 be rotated with big torque by quickening driven gear 22 and adding the bent axle 11 that is passed to driving engine E after speed drive gear 21 slows down.
In addition, by make the 1st power-transfer clutch C1 engage with the rotation constant speed of main shaft 13 be input to the sun and planet gear P that speed change is used, be input to the sun and planet gear P that speed change is used by after the 2nd power-transfer clutch C2 being engaged the rotation of main shaft 13 quickened by described accelerator module, thus, by the 1st power-transfer clutch C1 and the 2nd power-transfer clutch C2 are optionally engaged, can establish a plurality of gears.At this moment, be configured to countershaft 19 coaxially, therefore can make change-speed box T miniaturization being configured for the adding speed drive gear 21, quicken driven gear the 22, the 2nd power-transfer clutch C2 of accelerator module, the 1st tween drive shaft 20 of speed change and quickening output gear 23.
And,, the 1st motor/generator MG1 utilized the accelerator module that is used for speed change for being quickened to drive, therefore can realize the reduction of cost, moreover, because the 2nd power-transfer clutch C2 can will speed up driven gear 22 and the 1st tween drive shaft 20 combines, therefore, even the 2nd power-transfer clutch C2 is not engaged, thereby also can quicken to drive the raising generating efficiency to the 1st motor/generator MG1.
In addition, carry out two grades of speed changes owing to can make the gear ring 16 of the sun and planet gear P that speed change uses combine or make gear ring 16 to combine with housing 30 with the 2nd tween drive shaft 14 by drg B1 by the 3rd power-transfer clutch C3, therefore, the combination of engaging/combination that does not engage by the 3rd power-transfer clutch C3 and drg B1 and the engaging of the 1st power-transfer clutch C1 and the 2nd power-transfer clutch C2/do not engage can be established four-speed gear shift shelves altogether.
And, if the rotation after supposing to will speed up is input to the sun and planet gear P of change-speed box T, then extremely can obtain the converter speed ratio of needs for the rotational delay after will quickening, need excessive reduction ratio, thereby there is the worry that transmission efficiency reduces or change-speed box T maximizes, but,, therefore can realize the raising of transmission efficiency and the miniaturization of change-speed box T owing to do not need excessive reduction ratio according to present embodiment.
In addition, owing to be provided with the 2nd motor/generator MG2 that can rotate integratedly with the 2nd tween drive shaft 14, therefore, can make vehicle ' with the propulsive effort of simple structure by the 2nd motor/generator MG2, perhaps the propulsive effort by the 2nd motor/generator MG2 comes the propulsive effort of driving engine E is assisted, and perhaps the 2nd motor/generator MG2 is carried out regenerative brake and reclaims as electric energy with the kinetic energy with vehicle.
In addition, will speed up driven gear 22 and quicken output gear 23 separate configuration in the axial both sides of the 1st motor/generator MG1, the 1st motor/generator MG1 is disposed at the outer circumferential side of the 1st tween drive shaft 20, and the 2nd power-transfer clutch C2 is disposed at coaxially the 1st motor/generator MG1 interior all sides with the 1st motor/generator MG1 in the position of axial overlap, therefore can shorten the axial length of change-speed box T.
In addition and since the 1st power-transfer clutch C1 is disposed at coaxially the 2nd motor/generator MG2 interior all sides axially with the 2nd motor/generator MG2 position overlapped, therefore can shorten the axial length of change-speed box T.
The 3rd embodiment
Next, based on Figure 16～Figure 20 the 3rd embodiment of the present invention is described.
The change-speed box T of the 3rd embodiment is six speed, with the 1 fast gear～4 fast gear cooresponding 1 fast gear of the four-speed change-speed box T of the 2nd embodiment and the fast gear in 4 fast gear～6 on increased 2 fast gears and 3 fast gears newly.The member that increases in the change-speed box T of the 2nd embodiment in order to establish 2 fast gears and 3 fast gears is: reduction drive gear 31, and it is supported on main shaft 13 in the mode that can rotate freely; The 4th power-transfer clutch C4, it combines reduction drive gear 31 with main shaft 13; And deceleration driven gear 32, it is fixed in the 1st tween drive shaft 20 and meshes with reduction drive gear 31.
The establishment state of the establishment state of 1 fast gear and 4 fast gears～6 fast gears and the 1 fast gear～4 fast gears of the 2nd embodiment is (with reference to Figure 10～Figure 13) identical.In addition, variation has taken place at the 3rd embodiment in the title of the acceleration output gear 23 of the 2nd embodiment, become acceleration output gear 23 '.
If make the 4th power-transfer clutch C4 engaging, then the rotation of main shaft 13 via the 4th power-transfer clutch C4, reduction drive gear 31, deceleration driven gear the 32, the 1st tween drive shaft 20, acceleration output gear 23 ' and speed change input gear 24 be passed to the gear ring 16 of sun and planet gear P.At this moment, the number of teeth of the ratio of number of teeth deceleration driven gear 32 of reduction drive gear 31 is little, so the rotation of gear ring 16 is decelerated with respect to the rotation of main shaft 13.That is, if make the 2nd power-transfer clutch C2 engaging, then the rotation of gear ring 16 is accelerated with respect to the rotation of main shaft 13, if make the 4th power-transfer clutch C4 engaging, then the rotation of gear ring 16 is decelerated with respect to the rotation of main shaft 13.
Thereby Figure 17 shows the state that makes the 3rd power-transfer clutch C3 and the 4th power-transfer clutch C4 engaging establish 2 fast gears.Owing to thereby the 3rd power-transfer clutch C3 engaging makes the sun gear 15 of sun and planet gear P and gear ring 16 combinations make sun and planet gear P become lock-out state, therefore, the rotation of driving engine E with bent axle 11 → bumper 12 → main shaft 13 → the 4th power-transfer clutch C4 → reduction drive gear 31 → deceleration driven gear 32 → the 1st tween drive shaft 20 → acceleration output gears 23 ' → sun and planet gear P → the 1st speed change output gear 25 → the 2nd speed change output gear 26 → countershaft 19 of speed change input gear 24 → lock-out state → final driven wheel 27 → final driven gear 28 → diff D → axle drive shaft 29,29 path is passed to drive wheel W, W.
At this moment, neither quicken also not slow down, but slow down, establish the converter speed ratio 2 fast gears littler thus than 1 fast gear by reduction drive gear 31 and deceleration driven gear 32 at sun and planet gear P.
Thereby Figure 18 shows the state that makes the 1st power-transfer clutch C1 and the 4th power-transfer clutch C4 engaging establish 3 fast gears.Because the 4th power-transfer clutch C4 engaging, make main shaft 13 rotation by by the 4th power-transfer clutch C4, reduction drive gear 31, deceleration driven gear the 22, the 1st tween drive shaft 20, acceleration output gear 23 ' and the deceleration path that constitutes of speed change input gear 24 be passed to the gear ring 16 of sun and planet gear P, the rotation of gear ring 16 is decelerated with respect to the rotation of main shaft 13, on the other hand, because the 1st power-transfer clutch C1 engaging, main shaft 13 directly links by the sun gear 15 of the 2nd tween drive shaft 14 with sun and planet gear P.Consequently, the rotation of driving engine E with bent axle 11 → bumper 12 → main shaft 13 → the 4th power-transfer clutch C4 → reduction drive gear 31 → deceleration driven gear 32 → the 1st tween drive shaft 20 → acceleration output gears 23 ' → path of speed change input gear 24 → sun and planet gear P → the 1st speed change output gear 25 → the 2nd speed change output gear 26 → countershaft 19 → final driven wheel 27 → final driven gear 28 → diff D → axle drive shaft 29,29 is passed to drive wheel W, W.
At this moment, P slows down at sun and planet gear, also slows down by reduction drive gear 31 and deceleration driven gear 32, establishes the converter speed ratio 3 fast gears littler than 2 fast gears thus.
As mentioned above,, make the gear number of change-speed box T increase to six grades, can realize the action effect identical simultaneously with the 2nd embodiment from fourth gear according to present embodiment.
More than, embodiments of the present invention are illustrated, but the present invention can carry out various design modifications in the scope that does not break away from its main points.
For example, in the 1st embodiment with the gear ring 15 of the 1st sun and planet gear P1 as output link, with sun gear 16 as stationary member, with pinion carrier 17 as input link, but can suitably change the function of each member.
In addition, in the 1st embodiment, with the gear ring 19 of the 2nd sun and planet gear P2 as stationary member, with sun gear 20 as input link, with pinion carrier 21 as output link, but can suitably change the function of each member.
In addition, in the 1st embodiment, main the 2nd gear 26 can be combined with the 1st main shaft 13 by the 4th power-transfer clutch C4, and pair the 2nd gear 27 is fixed in countershaft 24, but, also main the 2nd gear 26 can be fixed in the 1st main shaft 13, and secondary the 2nd gear 27 can be combined with countershaft 24 by the 4th power-transfer clutch C4.
In addition, in the 2nd and the 3rd embodiment, with the sun gear 15 of sun and planet gear P as input link, with gear ring 16 as stationary member, with pinion carrier 17 as output link, but can suitably change the function of each member.

Claims (11)

1. hybrid drive, it possesses driving engine (E), the 1st motor/generator (MG1) and change-speed box (T),
Described hybrid drive is characterised in that,
Described change-speed box (T) possesses:
Input shaft (13; 13);
Output shaft (24; 19), it is with respect to described input shaft (13; 13) configuration abreast; And
Tween drive shaft (14; 14), it is configured in from described input shaft (13; 13) towards described output shaft (24; 19) on the power transfer path,
At described input shaft (13; 13) with described tween drive shaft (14; 14) be provided with the 1st power transfer path and the 2nd power transfer path between, described the 1st power transfer path is by acceleration mechanism (P1; 21,22) and add speed clutch (C2) and establish, described the 2nd power transfer path is by described acceleration mechanism (P1; 21,22) but by waiting speed clutch (C1) establishment,
At described acceleration mechanism (P1; 21, downstream 22) disposes described the 1st motor/generator (MG1), at described tween drive shaft (14; 14) downstream disposes main speed changing portion (P2; P).
2. hybrid drive, it possesses driving engine (E), the 1st motor/generator (MG1) and change-speed box (T),
Described hybrid drive is characterised in that,
On the 1st input shaft (13) of the propulsive effort input of the described driving engine of confession (E) of described change-speed box (T), dispose the 1st sun and planet gear (P1),
The 1st member (17) of described the 1st sun and planet gear (P1) always is connected with described the 1st input shaft (13),
The 2nd member (16) of described the 1st sun and planet gear (P1) is fixed in housing (31) in the mode that can not rotate,
The 3rd member (15) of described the 1st sun and planet gear (P1) is connected with described the 1st motor/generator (MG1),
Described the 1st sun and planet gear (P1) exports described the 3rd member (15) to after the rotation that is input to described the 1st member (17) from described the 1st input shaft (13) can being quickened, by engaging of the 1st power-transfer clutch (C1) that between the main speed changing portion (P2) of described the 1st member (17) and described change-speed box (T), be provided with, with the rotation constant speed of described the 1st input shaft (13) be passed to described main speed changing portion (P2), and, by at the engaging of the 2nd power-transfer clutch (C2) that is provided with between described the 3rd member (15) and the described main speed changing portion (P2), after being quickened, the rotation of described the 1st input shaft (13) is passed to described main speed changing portion (P2).
3. hybrid drive according to claim 2 is characterized in that,
Described main speed changing portion (P2) is made of the 2nd sun and planet gear (P2),
The 1st member (20) of described the 2nd sun and planet gear (P2) always is connected with the 2nd motor/generator (MG2) with the 2nd input shaft (14), described the 2nd input shaft (14) is embedded in the periphery of described the 1st input shaft (13) in freely the mode of can rotating relatively
The 2nd member (19) of described the 2nd sun and planet gear (P2) can be connected with described the 1st member (20) by the 3rd power-transfer clutch (C3), and the 2nd member (19) of described the 2nd sun and planet gear (P2) can be fixed in housing (31) by drg (B1)
The 3rd member (21) of described the 2nd sun and planet gear (P2) is connected with the output shaft (24) of described change-speed box (T).
4. hybrid drive according to claim 3 is characterized in that,
Described the 1st input shaft (13) and described output shaft (24) dispose parallel to each other, gear (26) that is fixed in the side in described the 1st input shaft (13) and the described output shaft (24) and gear (27) engagement that is supported on the opposing party in described the 1st input shaft (13) and the described output shaft (24) in freely the mode of can rotating relatively, the described gear (27) that supports in the mode freely of can rotating relatively can combine with the opposing party in described the 1st input shaft (13) and the described output shaft (24) by the 4th power-transfer clutch (C4).
5. according to claim 3 or the described hybrid drive of claim 4, it is characterized in that,
Described the 1st power-transfer clutch (C1) and described the 2nd power-transfer clutch (C2) and described the 1st motor/generator (MG1) be disposed at coaxially described the 1st motor/generator (MG1) interior all sides axially with described the 1st motor/generator (MG1) position overlapped, described the 3rd power-transfer clutch (C3) and described drg (B1) and described the 2nd motor/generator (MG2) be disposed at coaxially described the 2nd motor/generator (MG2) interior all sides axially and described the 2nd motor/generator (MG2) position overlapped.
6. according to any described hybrid drive in claim 3～claim 5, it is characterized in that,
Described the 1st sun and planet gear (P1) and described the 1st motor/generator (MG1) be disposed at coaxially described the 1st motor/generator (MG1) interior all sides axially with described the 1st motor/generator (MG1) position overlapped, described the 2nd sun and planet gear (P2) and described the 2nd motor/generator (MG2) be disposed at coaxially described the 2nd motor/generator (MG2) interior all sides axially with described the 2nd motor/generator (MG2) position overlapped.
7. hybrid drive, it possesses driving engine (E), the 1st motor/generator (MG1) and change-speed box (T),
Described hybrid drive is characterised in that,
Described change-speed box (T) possesses:
Input shaft (13);
Output shaft (19), it disposes abreast with respect to described input shaft (13);
The 1st tween drive shaft (20), it is embedded in the periphery of described output shaft (19) in freely the mode of can rotating relatively; And
The 2nd tween drive shaft (14), it is embedded in the periphery of described input shaft (13) in freely the mode of can rotating relatively,
The propulsive effort of described driving engine (E) inputs to described input shaft (13),
Be located at the 1st gear (21) and the 2nd gear (22) engagement of being located at described output shaft (19) of described input shaft (13), be passed to this output shaft (19) after thus the rotation of this input shaft (13) being quickened,
Periphery at described the 2nd tween drive shaft (14) disposes sun and planet gear (P),
The 1st member (16) of described sun and planet gear (P) is connected with the 3rd gear of being located at described the 1st tween drive shaft (20) (23,23 '),
The 2nd member (15) of described sun and planet gear (P) is connected with described the 2nd tween drive shaft (14),
The 3rd member (17) of described sun and planet gear (P) is connected with described output shaft (19),
Described input shaft (13) can combine with described the 2nd tween drive shaft (14) by the 1st power-transfer clutch (C1), described the 2nd gear (22) can combine with described the 1st tween drive shaft (20) by the 2nd power-transfer clutch (C2), and described the 2nd gear (22) can rotate integratedly with described the 1st motor/generator (MG1).
8. hybrid drive according to claim 7 is characterized in that,
Described the 1st member (16) of described sun and planet gear (P) can combine with described the 2nd tween drive shaft (14) by the 3rd power-transfer clutch (C3), and described the 1st member (16) of described sun and planet gear (P) can combine with housing (30) by drg (B1).
9. according to claim 7 or the described hybrid drive of claim 8, it is characterized in that,
Described hybrid drive possesses the 2nd motor/generator (MG2) that can rotate integratedly with described the 2nd tween drive shaft (14).
10. according to any described hybrid drive in claim 7～claim 9, it is characterized in that,
Described the 1st motor/generator (MG1) is disposed at the outer circumferential side of described the 1st tween drive shaft (20), described the 2nd gear (22) is disposed at an axial side of described the 1st motor/generator (MG1), and, described the 3rd gear (23,23 ') is disposed at the axial opposite side of described the 1st motor/generator (MG1), described the 2nd power-transfer clutch (C2) and described the 1st motor/generator (MG1) be disposed at coaxially described the 1st motor/generator (MG1) interior all sides axially with described the 1st motor/generator (MG1) position overlapped.
11. according to claim 9 or the described hybrid drive of claim 10, it is characterized in that,
Described the 1st power-transfer clutch (C1) and described the 2nd motor/generator (MG2) be disposed at coaxially described the 2nd motor/generator (MG2) interior all sides axially with described the 2nd motor/generator (MG2) position overlapped.
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CN106915247B (en) * 2015-12-28 2021-05-25 长城汽车股份有限公司 Hybrid power system and vehicle with same
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